CN104061732A - Refrigerator - Google Patents
Refrigerator Download PDFInfo
- Publication number
- CN104061732A CN104061732A CN201310445169.3A CN201310445169A CN104061732A CN 104061732 A CN104061732 A CN 104061732A CN 201310445169 A CN201310445169 A CN 201310445169A CN 104061732 A CN104061732 A CN 104061732A
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- China
- Prior art keywords
- mentioned
- temperature
- expansion valve
- cold
- refrigerating chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000007710 freezing Methods 0.000 claims abstract description 13
- 230000008014 freezing Effects 0.000 claims abstract description 12
- 239000003507 refrigerant Substances 0.000 claims description 25
- 238000001704 evaporation Methods 0.000 claims description 20
- 238000001816 cooling Methods 0.000 claims description 9
- 239000012071 phase Substances 0.000 claims description 7
- 239000012808 vapor phase Substances 0.000 claims description 7
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 238000009833 condensation Methods 0.000 claims description 5
- 230000005494 condensation Effects 0.000 claims description 5
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 abstract 6
- 239000012530 fluid Substances 0.000 abstract 1
- 230000008020 evaporation Effects 0.000 description 7
- 239000007788 liquid Substances 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 229920006395 saturated elastomer Polymers 0.000 description 6
- 239000007791 liquid phase Substances 0.000 description 5
- 230000009467 reduction Effects 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000009834 vaporization Methods 0.000 description 3
- 230000008016 vaporization Effects 0.000 description 3
- VQTUBCCKSQIDNK-UHFFFAOYSA-N Isobutene Chemical compound CC(C)=C VQTUBCCKSQIDNK-UHFFFAOYSA-N 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000035488 systolic blood pressure Effects 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
- F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/01—Heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/073—Linear compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2511—Evaporator distribution valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention relates to a refrigerator comprising a main body including a refrigerating compartment at a temperature higher than a freezing temperature and a freezing compartment at a temperature lower than the freezing temperature, a deep-freezing storage chamber within the main body at a temperature lower than that of the freezing compartment. The refrigerator further includes a compressor compressing refrigerating fluid into high temperature and high pressure refrigeration agent, a condenser connected to an outlet-side of the compressor and condensing the high temperature and high pressure refrigeration agent, a first expansion valve connected to an outlet-side of the condenser and enabling the refrigeration agent to be expanded into two-phase low temperate and low pressure refrigeration agent, a first evaporator connected to an outlet-side of the first expansion valve and changing the refrigeration agent into a gaseous agent with low temperature and low pressure, and a heater disposed outside the first expansion valve and suppying heat for the first expansion valve to enable the steam temperature of the refrigeration agent to be lower than interior temperature of the freezing compartment.
Description
The cross reference of related application
The priority of the korean patent application that it is 10-2013-0031036 that the application requires in the application number of submitting on March 22nd, 2013, its full content is by reference in conjunction with in this application.
Technical field
The present invention relates to refrigerator.
Background technology
Refrigerator, can comprise with frozen state and preserve the refrigerating chamber of food and with freezing state, preserve the refrigerating chamber of food for preserve the household electrical appliance of food with low-temperature condition as a kind of.
Recently, people are to having the demand of refrigerator of independent storeroom at short notice food being cooled to ultralow temperature in continuous increase.To achieve these goals, following structure had been proposed in the past: independent extremely cold storeroom is set in the inside of refrigerating chamber, by connecting the cold air stream of extremely cold storeroom and vaporization chamber, to extremely cold storeroom, independently supplies with the cold air of vaporization chamber.This extremely cold storeroom in the past can only be supplied to the cold air of vaporization chamber to extremely cold storeroom one side individually, thereby is not subject to the impact of refrigerating chamber and temperature of refrigerating chamber, the temperature of extremely cold storeroom can be reduced to the temperature lower than refrigerating chamber.
And common refrigerator is used R-600a isobutene cold-producing medium, and the temperature of evaporimeter is dropped to minimum subzero 40 ℃～42 ℃.But the temperature requirement of extremely cold storeroom drops to the temperature lower than described temperature, that is, subzero 50 ℃ is not enough for this possesses independent extremely cold storeroom.
In order to meet this extremely subcooled requirement, with contact, adopted a kind of mode that makes expansion valve carry out heat exchange with the suction pipe that is connected evaporimeter and compressor.At length, through the heat exchange of suction pipe and expansion valve, reduce the mode of evaporating temperature, although the temperature of the cold-producing medium of process expansion valve can further reduce, and amount of heat absorption increases, thereby there is the effect that refrigerating capacity improves, but because evaporating pressure self does not reduce, therefore limited in reduction evaporating temperature.
As additive method, can use the expansion valve that diameter is less, in this case, although have advantages of that evaporating pressure further reduces, but there is while the temperature of extremely cold storeroom being reduced to design temperature from evaporimeter absorption heat the shortcoming that the saturated delivery rate of cold-producing medium reduces.At length, the saturated delivery rate reduction of cold-producing medium refers to, becomes the amount minimizing of saturated gas through the cold-producing medium of evaporimeter.This means, enter the amount of liquid refrigerant of gas-liquid segregating unit more than the amount of gaseous refrigerant, its result, the possibility that liquid refrigerant flows into compressor increases.To cause like this in whole freeze cycle, further increase the result that systolic pressure and evaporation are pressed.And liquid refrigerant flows into compressor also can cause the performance reduction of compressor or the danger of damage.
Summary of the invention
The present invention proposes in order to improve above-mentioned shortcoming, and its object is, and provide a kind of and not only the temperature of extremely cold storeroom is reduced manyly than in the past, but also can be by the minimized refrigerator of the damage of compressor.
For realizing the refrigerator of the embodiments of the invention of object as above, comprise: body, comprise at least one in refrigerating chamber and refrigerating chamber, wherein, above-mentioned refrigerating chamber maintains the temperature higher than freezing temperature, and above-mentioned refrigerating chamber maintains the temperature lower than freezing temperature; Extremely cold storeroom, is positioned at the inside of above-mentioned body, and the internal temperature of above-mentioned extremely cold storeroom maintains the temperature lower than the temperature of above-mentioned refrigerating chamber; Compressor, becomes refrigerant compression the cold-producing medium of HTHP; Condenser, is connected with the outlet side of above-mentioned compressor, for the cold-producing medium of HTHP is carried out to condensation; The first expansion valve, is connected with the outlet side of above-mentioned condenser, for making cold-producing medium be expanded to the two phase refrigerant of low-temp low-pressure; The first evaporimeter, is connected with the outlet side of above-mentioned the first expansion valve, for cold-producing medium being changed into the vapor phase refrigerant of low-temp low-pressure; And heater, be arranged at the outside of above-mentioned the first expansion valve, for supplying with heat to above-mentioned the first expansion valve, the evaporating temperature of cold-producing medium is reduced to the temperature lower than the internal temperature of above-mentioned refrigerating chamber.
According to forming the refrigerator of structure as mentioned above, on the expansion valve being connected with the entrance side of evaporimeter with extremely cold storeroom, independent heater is installed, make evaporating pressure than in the past, reduce manyly, have advantages of and the temperature of evaporimeter can be reduced to minimum subzero 50 degree.And, can not cause changing the phenomenon of the saturated delivery rate reduction of the cold-producing medium producing in the diameter situation of expansion valve, so there is performance or the problem of damage that compressor does not occur to reduce.
Accompanying drawing explanation
Fig. 1 means the figure of freeze cycle of the refrigerator of embodiments of the invention.
Fig. 2 be to the freeze cycle of embodiments of the invention and in the past common freeze cycle compare the p-h line chart of expression.
The specific embodiment
In the following detailed description of preferred embodiment being carried out with reference to exemplary accompanying drawing, also can implement concrete preferred embodiment of the present invention.Detailed description by embodiment makes those skilled in the art can implement the present invention, and should be appreciated that within not departing from its spirit or scope of the present invention, can carry out the variation of logical construction, machinery, electricity and chemical property.For fear of unnecessary details, so that those skilled in the art can implement the present invention, this explanation will be omitted some information well known by persons skilled in the art.Therefore, detailed description below does not have limiting meaning, and scope of the present invention is only defined by described technical scheme.
Below, with reference to accompanying drawing, the refrigerator of embodiments of the invention is elaborated.
The refrigerator of embodiments of the invention comprises: body, comprise at least one in refrigerating chamber and refrigerating chamber, and wherein, above-mentioned refrigerating chamber maintains the temperature higher than freezing temperature, and above-mentioned refrigerating chamber maintains the temperature lower than freezing temperature; Extremely cold storeroom, is positioned at the inside of above-mentioned body, and the internal temperature of above-mentioned extremely cold storeroom maintains the temperature lower than the temperature of above-mentioned refrigerating chamber; Compressor, becomes refrigerant compression the cold-producing medium of HTHP; Condenser, is connected with the outlet side of above-mentioned compressor, for the cold-producing medium of HTHP is carried out to condensation; The first expansion valve, is connected with the outlet side of above-mentioned condenser, for making cold-producing medium be expanded to the two phase refrigerant of low-temp low-pressure; The first evaporimeter, is connected with the outlet side of above-mentioned the first expansion valve, for cold-producing medium being changed into the vapor phase refrigerant of low-temp low-pressure; And heater, be arranged at the outside of above-mentioned the first expansion valve, for supplying with heat to above-mentioned the first expansion valve, the evaporating temperature of cold-producing medium is reduced to the temperature lower than the internal temperature of above-mentioned refrigerating chamber.
And, the invention is characterized in, above-mentioned heater is arranged to the form contacting with the outer peripheral face of above-mentioned the first expansion valve.
And the above-mentioned compressor of refrigerator of the present invention comprises Linearkompressor.
And, the invention is characterized in, the cold air that above-mentioned the first evaporimeter is supplied with for the above-mentioned extremely cold storeroom of subtend carries out cooling.
And the refrigerator of embodiments of the invention also comprises: one or more the second evaporimeters, to some in above-mentioned refrigerating chamber or refrigerating chamber or all carry out cooling; And one or more the second expansion valves, be connected with the entrance side of above-mentioned one or more the second evaporimeters respectively.
And, above-mentioned the first expansion valve and above-mentioned one or more the second expansion valve are connected in parallel, the refrigerator of embodiments of the invention also comprises switching valve, and described switching valve is arranged at the branch location of above-mentioned the first expansion valve and the second expansion valve, for changing the flow direction of cold-producing medium.
Fig. 1 means the figure of freeze cycle of the refrigerator of the embodiment of the present invention.
With reference to Fig. 1, the freeze cycle 10 of the refrigerator of the embodiment of the present invention comprises: compressor 11, becomes refrigerant compression the gaseous state of HTHP; Condenser 12, is arranged on the outlet side of above-mentioned compressor 11, becomes mutually the liquid phase refrigerant of HTHP for the vapor phase refrigerant of the HTHP that makes to form by above-mentioned compressor 11 compressions; Expansion valve 14,15, is arranged on the outlet side of above-mentioned condenser 12, for the liquid phase refrigerant by the cooling HTHP forming of above-mentioned condenser 12 being expanded to the two phase refrigerant of low-temp low-pressure; Evaporimeter 16,17, is arranged on the outlet side of above-mentioned expansion valve 14,15, for the two phase refrigerant of the low-temp low-pressure forming by above-mentioned expansion valve phase transformation being become mutually to the vapor phase refrigerant of low-temp low-pressure.
At length, above-mentioned compressor 11 comprises Linearkompressor, and, also comprise constant speed compressor or the inverter compressor of other types.In the situation that above-mentioned compressor 11 is Linearkompressor, control above-mentioned compressor 11 and in extremely cold cooling procedure, carry out top dead-centre (Top Dead Center) running.
And above-mentioned condenser 12 is housed in the Machine Room of rear side of refrigerator, to indoor air exhaust heat conventionally.And, between above-mentioned condenser 12 and above-mentioned expansion valve 14,15, the switching valve 13 that comprises triple valve can be set.In the main evaporator 16 for refrigerated compartment and refrigerating chamber and the structure that is connected in parallel for the extremely cold evaporimeter 17 of cooling extremely cold storeroom, above-mentioned switching valve is for changing the flow direction of cold-producing medium.According to the number of evaporimeter, can use triple valve or cross valve.For example, use a main evaporator, by conversion, connect the cold air stream of refrigerating chamber and refrigerating chamber, control independently in the situation of temperature of each storeroom, triple valve can be installed.On the contrary, evaporimeter for refrigerating chamber, refrigerating chamber being set respectively with in evaporimeter and extremely cold evaporimeter structure that they are connected in parallel, can utilize cross valve to change the flow direction of cold-producing medium.
Illustrate in the present embodiment, take following embodiment as example describes, that is, for refrigerated compartment and refrigerating chamber, use a main evaporator 16, and be connected in parallel for the independent extremely cold evaporimeter 17 of cooling extremely cold storeroom.Thus, at the entrance side of above-mentioned main evaporator 16 and extremely cold evaporimeter 17, be connected respectively main expansion valve 15 and extremely cold expansion valve 14, above-mentioned expansion valve 15 is connected in parallel with the outlet side of above-mentioned switching valve 13.
And, at the outer peripheral face of above-mentioned extremely cold expansion valve 14, independent heater 18 is installed, be used as a kind of the temperature through the cold-producing medium of above-mentioned extremely cold expansion valve 14 being reduced to more to the scheme lower than the temperature of refrigerating chamber.Above-mentioned heater 18 is worked under the operation mode of cooling extremely cold storeroom, when extremely cold storeroom is cooled to design temperature, controls above-mentioned heater 18 it is quit work.
And, in the outside of above-mentioned condenser 12 and evaporimeter 16,17, condenser fan and evaporating fan are installed respectively, make room air and cold-producing medium or storeroom air and cold-producing medium carry out heat exchange.
Fig. 2 compares the p-h line chart of expression to the freeze cycle of the embodiment of the present invention and common freeze cycle in the past.
With reference to Fig. 2, common freeze cycle is in the past according to compress → condensation → expansion → evaporation process of the order of a → b → c → d.
On the contrary, the freeze cycle of the embodiment of the present invention, that is, on the outer peripheral face of extremely cold expansion valve 14, the freeze cycle of mounting heater 18 is according to compress → condensation → expansion → evaporation process of the order of e → f → c → g.
As shown in p-h line chart, if while being arranged on 18 work of heater on extremely cold expansion valve 14, through the cold-producing medium of extremely cold expansion valve 14 just with more lower than the evaporation pressure drop low-pressure of freeze cycle generation in the past.At length, if evaporation pressure drop when low, evaporating temperature also together reduces, and by evaporating temperature, reduces, and can make the cold air temperature of extremely cold storeroom reduce more lower than temperature in the past.
Common freeze cycle in the past shown in the line chart of Fig. 2 is not for there is no the cycle diagram when expansion valve arranges any heat-exchanging part, suction pipe and expansion valve are carried out in the structure of heat exchange, heat is transferred in the cold-producing medium through suction pipe by the cold-producing medium through expansion valve, its result, the amount of the vapor phase refrigerant in the cold-producing medium of inflow compressor can increase.And the temperature of the cold-producing medium of process expansion valve reduces, and the enthalpy line (c-d line) of cold-producing medium is moved to the left in the enterprising step of line chart.So the enthalpy of the cold-producing medium of evaporator inlet reduces, its result, along with the suction heat increase of evaporimeter, the effect of bringing refrigerating capacity to improve.But, even if utilize suction pipe to carry out heat exchange, because of evaporation press constant, even and exist refrigerating capacity to increase, also cannot and then reduce the shortcoming of the cold air temperature of extremely cold storeroom.
And, in the situation that use diameter is less than the extremely cold expansion valve of the diameter of main expansion valve, the state point (d point) of the cold-producing medium while finishing that not only expands,, the evaporation at extremely cold evaporator inlet place is pressed and can further be reduced, and the enthalpy of extremely cold evaporator inlet also can increase.That is, the d point on p-h line chart moves to lower right side.Its result, the temperature of cold-producing medium further reduces, and this is perhaps conducive to further reduce the temperature of extremely cold storeroom.But exist and therefore cause the shortcoming that becomes mutually the amount minimizing of vapor phase refrigerant through the liquid phase refrigerant in the cold-producing medium of evaporimeter.That is, suppose from room air, to absorb the energy of identical heat through the cold-producing medium of evaporimeter, the amount that is become mutually the cold-producing medium of gas phase from liquid phase can reduce.That is, this means that the saturated delivery rate of cold-producing medium will reduce, thus, the possibility that liquid phase refrigerant flows into compressor perhaps can increase.
As embodiments of the invention propose, in the situation that the surperficial mounting heater 18 of extremely cold expansion valve 14, under perfect condition (ideal state), the exit point of extremely cold expansion valve (or exit point of extremely cold evaporimeter) d will be mobile to g point.In actual freeze cycle, some g will be positioned at and then mobile point to the right.
Suppose that evaporimeter absorbs the energy of identical heat, compare with situation about changing under the condition of expansion valve diameter, the entrance of compressor, says closely, according to the mass dryness fraction (quality) of the cold-producing medium of the gas-liquid segregating unit porch of the embodiment of the present invention, can further increase.The saturated delivery rate that this means cold-producing medium can not reduce, thereby liquid refrigerant flows into the possibility of compressor, can reduce significantly.
As shown in the figure, the heater 18 proposing in the present invention is attached to above-mentioned extremely cold expansion valve 14, make evaporating temperature and evaporating pressure reduction significantly compared with the past through the cold-producing medium of above-mentioned extremely cold expansion valve 14, the temperature that can access thus extremely cold storeroom can be cooled in the effect that is starkly lower than freezer temperature.In other words, through the cold-producing medium of the expansion valve of mounting heater not, can only be reduced to the temperature of 40 degrees below zero left and right, but can be reduced to minimum subzero 50 degree through the cold-producing medium of the expansion valve of heater is installed.
Claims (6)
1. a refrigerator, is characterized in that, comprising:
Body, comprises at least one in refrigerating chamber and refrigerating chamber, and wherein, above-mentioned refrigerating chamber maintains the temperature higher than freezing temperature, and above-mentioned refrigerating chamber maintains the temperature lower than freezing temperature;
Extremely cold storeroom, is positioned at the inside of above-mentioned body, and the internal temperature of above-mentioned extremely cold storeroom maintains the temperature lower than the temperature of above-mentioned refrigerating chamber;
Compressor, becomes refrigerant compression the cold-producing medium of HTHP;
Condenser, is connected with the outlet side of above-mentioned compressor, for the cold-producing medium of HTHP is carried out to condensation;
The first expansion valve, is connected with the outlet side of above-mentioned condenser, for making cold-producing medium be expanded to the two phase refrigerant of low-temp low-pressure;
The first evaporimeter, is connected with the outlet side of above-mentioned the first expansion valve, for cold-producing medium being changed into the vapor phase refrigerant of low-temp low-pressure; And
Heater, is arranged at the outside of above-mentioned the first expansion valve, for supplying with heat to above-mentioned the first expansion valve, the evaporating temperature of cold-producing medium is reduced to the temperature lower than the internal temperature of above-mentioned refrigerating chamber.
2. refrigerator according to claim 1, is characterized in that, above-mentioned heater is arranged to the form contacting with the outer peripheral face of above-mentioned the first expansion valve.
3. refrigerator according to claim 2, is characterized in that, above-mentioned compressor comprises Linearkompressor.
4. refrigerator according to claim 2, is characterized in that, the cold air that above-mentioned the first evaporimeter is supplied with for the above-mentioned extremely cold storeroom of subtend carries out cooling.
5. refrigerator according to claim 4, is characterized in that, also comprises:
One or more the second evaporimeters, to some in above-mentioned refrigerating chamber or refrigerating chamber or all carry out cooling; And
One or more the second expansion valves, are connected with the entrance side of above-mentioned one or more the second evaporimeters respectively.
6. refrigerator according to claim 5, is characterized in that,
Above-mentioned the first expansion valve and above-mentioned one or more the second expansion valve are connected in parallel,
Also comprise switching valve, described switching valve is arranged at the branch location of above-mentioned the first expansion valve and the second expansion valve, for changing the flow direction of cold-producing medium.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020130031036A KR20140115837A (en) | 2013-03-22 | 2013-03-22 | Method for controlling refrigerator |
| KR10-2013-0031036 | 2013-03-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104061732A true CN104061732A (en) | 2014-09-24 |
Family
ID=49554093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310445169.3A Pending CN104061732A (en) | 2013-03-22 | 2013-09-26 | Refrigerator |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20140284025A1 (en) |
| EP (1) | EP2781860A3 (en) |
| KR (1) | KR20140115837A (en) |
| CN (1) | CN104061732A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106595139A (en) * | 2016-12-27 | 2017-04-26 | 珠海市银岭冷冻设备有限公司 | Refrigerating system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109974345A (en) * | 2019-03-04 | 2019-07-05 | 中国科学院理化技术研究所 | Gas compensating type compressor and the compression circulatory system |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3638447A (en) * | 1968-09-27 | 1972-02-01 | Hitachi Ltd | Refrigerator with capillary control means |
| CN2663885Y (en) * | 2003-10-31 | 2004-12-15 | 广东科龙电器股份有限公司 | An energy-saving refrigerator |
| US20100154443A1 (en) * | 2007-03-29 | 2010-06-24 | Chan Ho Chun | Control method of refrigerator |
| US20100162747A1 (en) * | 2008-12-31 | 2010-07-01 | Timothy Allen Hamel | Refrigerator with a convertible compartment |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5231847A (en) * | 1992-08-14 | 1993-08-03 | Whirlpool Corporation | Multi-temperature evaporator refrigerator system with variable speed compressor |
| US5715693A (en) * | 1996-07-19 | 1998-02-10 | Sunpower, Inc. | Refrigeration circuit having series evaporators and modulatable compressor |
| JP3583570B2 (en) * | 1996-11-26 | 2004-11-04 | シャープ株式会社 | refrigerator |
| WO2006064601A1 (en) * | 2004-12-15 | 2006-06-22 | Sharp Kabushiki Kaisha | Refrigerator |
| DE102005045585A1 (en) * | 2005-05-11 | 2006-11-16 | Liebherr-Hausgeräte Ochsenhausen GmbH | Cooling and / or freezing device and method for controlling the same |
-
2013
- 2013-03-22 KR KR1020130031036A patent/KR20140115837A/en not_active Application Discontinuation
- 2013-09-26 CN CN201310445169.3A patent/CN104061732A/en active Pending
- 2013-10-16 US US14/055,424 patent/US20140284025A1/en not_active Abandoned
- 2013-11-08 EP EP13192107.4A patent/EP2781860A3/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3638447A (en) * | 1968-09-27 | 1972-02-01 | Hitachi Ltd | Refrigerator with capillary control means |
| CN2663885Y (en) * | 2003-10-31 | 2004-12-15 | 广东科龙电器股份有限公司 | An energy-saving refrigerator |
| US20100154443A1 (en) * | 2007-03-29 | 2010-06-24 | Chan Ho Chun | Control method of refrigerator |
| US20100162747A1 (en) * | 2008-12-31 | 2010-07-01 | Timothy Allen Hamel | Refrigerator with a convertible compartment |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106595139A (en) * | 2016-12-27 | 2017-04-26 | 珠海市银岭冷冻设备有限公司 | Refrigerating system |
Also Published As
| Publication number | Publication date |
|---|---|
| US20140284025A1 (en) | 2014-09-25 |
| EP2781860A2 (en) | 2014-09-24 |
| EP2781860A3 (en) | 2015-10-28 |
| KR20140115837A (en) | 2014-10-01 |
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Application publication date: 20140924 |